Movable vane compressor or motor



A. LATHAM, JR

MOVABLE VANE COMPRESSOR OR MOTOR Jan. 2, 1951 5 Sheets-Sheet 1 Filed Jan. 15, 1944 llu H! wlm m,

, INVENTOR B-Y %l/ 47 .12 14- ATTO R N E Jan. 2, 1951 A. LATHAM, JR 2,536,851

MOVABLE VANE COMPRESSOR 0R MOTOR Filed Jan. 15, 1944 l '5 Sheets-Sheet 2 INVENTOR \dzwmfadw zu BY AzTORNEY g 5 Sheets-Sheet 5 Filed Jan. 15, 1944 j' I INVENTOR 6/ BY Jan. 2, 1951 A. LATHAM, JR

MOVABLE VANE COMPRESSOR OR MOTOR 5 Sheets-Sheet 4 Filed Jan. 15, 1944 Ii & INVENTOR T =1- wwm zv TTORiEY Jan. 2, 1951 A. LATHAM, JR 2,536,851

MOVABLE VANE COMPRESSOR 0R MOTOR Filed Jan. 15, 1944 5 Sheets-Sheet 5 INVENTOR BY y) Patented Jan. 2, 1&51

MOVABLE VANE COMPRESSOR OR MOTOR Allen Latham, Jr., Jamaica Plain, Mass, assignor to Arthur D. Little, Inc., Cambridge, Mass., a corporation of-Massachusetts Application January 15, 1944, Serial No. 518,357

. 15 Claims. (01.230-157) This invention relates to compressoror motor apparatus. It relates especially to compressor or motor apparatus of the rotary movable vane type.

Heretofore rotary compressor or motor apparatus has been proposed which comprises a rotor within suitable confining means that has inlet and outlet ports therein and that presents an internal cylindrical surface. The rotor is mounted for rotation about an axis that is offset from, and is parallel to, the axis of the internal cylindrical surface of the confining means, the rotor being positioned so that the periphery of the rotor is in juxtaposition with a limited portion of the confining means that is between the inlet and outlet ports, leaving a crescent shaped chamber between the periphery of the rotor and the confining means. A plurality of vane units are dis-. posed transversely to the rotor and extend through the periphery of the rotor in slidable relation thereto so that the ends terminate in close proximity to the inner surface of the confining means and provide barriers across the crescent shaped chamber. The vane units are mounted for rotation about an axis that is :coincident with the axisof the inner cylindrical surface of the confining means. When the rotor is positively driven the apparatus can be used as a compressor for compressing a gas or a vapor,

during operation of the apparatus as a compressor or is used to take off power during operation of the apparatus as a motor, this shaft means is referred to as the power shaft means of the apparatus. And since the apparatus can be used either as a compressor or as a motor, the apparatus is referred to for the sake of brevity as compressor or motor apparatus.

It is a purpose of this invention to provide improvements in compressor or motor apparatus of the character referred to.

One of the features of this invention resides in" the provision of guide means in combination with the vane units for effecting more precise movement of the vane units relative to the other parts of the apparatus, thus minimizing vibration, noise and wear and increasing the efiiciency of the apparatus.

Another feature of this invention resides in the sealing means for sealing the crescent shaped chamber between the periphery of the rotor and the interior of the confining means at the juncture between the rotor and the confining means. According to this invention a liquid seal is provided between these relatively movable parts, the

liquid being supplied to a channel which is imtegral with the confining means and into which suitable flange means integral with the rotor penetrates. During operation of the apparatus centrifugal force maintains the liquidseal and highly effective scaling is afforded .while reducing friction and wear to a minimum.

Another feature of this invention resides in the lubrication of the bearing means for the vane units and for the rotor bearing. According to this invention a liquid, preferably water, is fed to these hearings and means are provided for directing the liquid escaping from the bearings out of the apparatus. In the case of the vane unit bearings, the liquid escapes into the rotor and means are provided for directing the liquid out of the rotor and out of the apparatus.

Further features of this invention relate to the method and means for employing liquid, preferably liquid used for lubrication and sealing purposes, to cool the working parts of the compressor or motor apparatus. Another feature of the invention relates to the novel combination of bearing members, whereby bearing means is afforded that is adapted for use under severe operating conditions that cause excessively rapid deterioration of ordinary bearings.

A further feature of this invention resides in the use of the rotor of the compressor or motor apparatus as a flywheel directly connected with the crank shaft of an engine.

. The foregoing features of this invention may be availed of separately and in such case constitute separate and independent features of this invention. It is preferable, however, to employ the foregoing features of this invention in combination; Thus, and as will be described more in detail hereinbelow, it is preferable to supply lubricant liquid, e. g., water, to the bearings that are specially designed according to this inven tion, discharge the' liquid into the rotor where it; serves, to lubricate the guide means for the vane units, and then direct the liquid from the rotor and into the sealing channel constituting part of the sealing means before the liquid is directed out of the apparatus, the liquid at the same time serving to cool the working parts of the apparatus.

Further features, purposes, and advantages of this invention will be apparent in connection with the following description of the exemplary em bodiment of this invention which is shown in the aocompaying drawings, wherein;

Fig. 1 is a front elevation of compressor or motor apparatus embodying this invention;

Fig. 2 is a side sectional elevation of the compressor or motor apparatus taken on the line 2-2 of Fig. 1;

Fig. 3 is a front sectional elevation of the com- 7 pressor or motor apparatus taken on the line 3-3 of Fi 2;

Fig. 4 is a side sectional elevation on an enlarged scale of the shaft means for carrying the vane units showing the channels therein for lubricant;

Fig. 5 is a cross-section of the shaft means shown in Fig. l and taken on the line 55 of Fig. 4;

Fig. 6 is a section taken on the line Ii'6 of Fig. 2 showing one of the rotor bearings and the means for holding the shaft for the vane units;

Fig. '7 is a front elevation detail, partly in section, taken on the line 'I"! of Fig. 2;

Figs. 8, 9 and 10 are respectively separate elevations of the three vane units of the apparatus; and

Fig. 11 is a front elevation, on a reduced scale, of one of the seal plates forming part of a sealing means of the apparatus.

In the following description of the embodiment of this invention shown in the drawings, the apparatus is arranged for purposes of illustration as appropriate for use as. a compressor operable for compressing water vapor and, for the sake of brevity, the apparatus shown in the drawings will be referred to as a compressor.

The compressor is shown secured to a suitable support H), which may, for example, be the end of a crank case of an engine having the power shaft ll rotatably mounted in the bearing 15. The back cover plate I2 of the compressor is secured to'the support ill by any suitable means such as the bolts !3.

The port ring it is secured to the back plate [2 by the bolts 55 with the seal plate I6 assembled therebetween. The port ring [4 presents an internally cylindrical surface, and has-an inlet port l8 and an outlet port l9 therein. Secured to the other side of the port ring Id by bolts is the front cover plate 2 l, with the seal plate l6 assembled therebetween. The port ring, together with the seal plates 16 and iii, provide confining means presenting an internally cylindrical surface, this confining means cooperating with the periphery of the rotor to provide a crescent shaped chamber for the compression of vapor as will be described below. While the confining means has been shown as composed of a specific arrangement of parts, it is apparent that the confining means can be constructed in other Ways. The seal plates l6 and I6 are identical, and one of them, namely, the seal plate 16, is shown separately, but on a reduced scale, in Fig. 11. It may be noted that the outer and inner edges are not concentric, the outer edge corresponding to that of the port ring while the inner curvature corresponds to that of the rotor, the axis of which is offset from that of the inner cylindrical surface of the port ring.

Within the port ring is the rotor which is indicated generally by the reference character 22. The rotor has an end wall 23 which is secured to the hub 24 of power shaft I i by bolts 25 the heads of which are counter-sunk in the recesses 18 in the end wall 23. A steam seal packing means 26 is provided between the exterior of the rotor end wall 23 and the back plate 12 and the support it, and a packing 12 may be provided when, for example, the power shaft l l is the crank shaft of an internal combustion engine and it is desired to provide a seal against leakage of oil from the crank case. Extending from the end wall 23 are three rotor segments 2! which collectively present a peripheral cylindrical surface. Secured to the ends of rotor segments 2? by bolts 28 is the ring shaped rotor end wall 29, which in turn has secured thereto by bolts 38 the rotor journal 3|. The rotor bushing 32 is interposed between 'the rotor journal 3! and the journal housing 33 which is part of the front cover plate 2 i.

1 The axis of rotation of the rotor 22 as determined by' the shaft 'II on one side of the rotor and the rotor journal 3| on the other side of the rotor is parallel to, but offset from the axis of the internal cylindrical surface of the port ring that constitutes part of the confining means above referred to. The dimensions of the parts are such that the rotor comes into close proximity to the region of the port ring indicated by the reference character a in Fig. 3 with a very small clearance therebetween. Preferably the curvature of the region of the port ring indicated as a conforms to the curvature of the cylindrical periphery of the'rotor rather than the curvature of the inner cylindrical surface of the balance of the port ring so as to provide a region of substantial length that affords a seal between the inlet and-outlet ports of the seal ring ratherthan merely a line of sealing abutment between the periphery of the rotor and the inner surface of the port ring. The balance of the periphery of the rotor is spaced from the inner surface of the port ring leaving a crescent shaped chamber therebetween. The inner surface of the port ring is characterized by the internal cylindrical surface H, and the port ring and confining means are referred to hereinas presenting an internal cylindrical surface notwithstanding the occurrence therein of the inlet and outlet ports and the possible occurrence of a region such as the region a where the curvature does not conform to the balance of internal cylindrical surface. When reference is made to the axis'of the internal cylindrical surface of the port ring or of the confining'means, the reference is to the axis of the cylindrical surface ll.

Coincident with the axis'of the internal cylindrical surface of the port ring is the'vane carrying shaft 34. This shaft is fixedly supported by the shaft hub 35 which is secured to the end of journal housing 33 by bolts 36. The shaft 34 can be kept from rotating relative to the hub 35 by the set screw 31 and preferably is provided with a tapered end portion 13 that extends into the counter-sunk recess Him the center of the end wall 23.

Rotatable about the vane carrying shaft are vane units which are indicated generally by the reference characters 38a, 38b, and 330 respectively. The vane unit 38a (see Fig. 8) is provided with a hub 39a through which the shaft 34 passes, anti-friction bushing means 490, being provided between the shaft 34 and the hub. Integral with the hub 39a and extending therefrom is the vane carrying arm Ma. from the end of which extends the plate-like vane-member 42a. 0m the oppo site side of the hub from the vane carrying arm.

shown in Fig. 2 the bearing means for the vane units fit together on shaft 34 for rotation of the vane units in the same axial position relative to the shaft 34.

The vanes 42a, 42b and 42c extend through the rotor between the rotor segments 21 in slidable relation therewith and, in order to provide a sealing means which permits a certain amount of oscillation of the vanes relative to the rotor wall, the ends of the segments 21 have cylindrical recesses 46 therein into which are fitted for slidable rotation semi-cylindrical pivot blocks 31, the plane surfaces of which are in sliding engagement with the surfaces of the vanes 42a, 42b and 420. The vanes 42a, 42b and 420 extend to close proximity with the internal cylindrical surface I? of the confining means with very close clearance and are preferably provided with shoes 48a, 48b and 480 at the end that can be retracted into grooves 49 in the surface of the rotor between the segments. The bearing means for the vane units prevents centrifugal force from urging the ends of the vanes against the internal cylindrical surface l'l. The lateral dimensions of the vanes 42a, 42b and 42c are such that the vanes provide a barrier across the crescent shaped chamber between the periphery of the rotor and the confining means at all positions of the vanes relative to the chamber between the inlet and outlet ports. The surface I? between the inlet and outlet ports is of at least sufiicient extent so that a completely closed chamber will be provided between two vanes in the region of the surface ll.

It is usually desired to provide a channel 50 in the port ring l4 that constitutes a continuation or extension of the inlet port, so as to facilitate sweeping the vapor into the crescent shaped chamber between the rotor and the port ring. A similar channel 52, but of lesser extent, is provided at the outlet port. The extent of the channel 52 determines the degree to which the vapor is compressed prior to its release.

It is one of the features of this invention that the vane units are provided with guides means for maintaining them in their proper axial position. In the embodiment shown in the drawings, the guide means consist of guide members 53 which are button-like and are held in position by the pins 54 and 54. The pins 54 are conveniently formed at the ends of the counterweight bars 44a, 44b and Q40. The pins 54' are integral with vane carrying arms Ma, Mb and M and preferably are spaced from the axis of the shaft by a distance corresponding to the distance by which pins 54 are spaced from the axis of shaft 34. The guide members 53 are disposed so as to be immediately proximate to the inner surface of the end walls 23 and 29 of the rotor for actual or virtual contact therewith. In either event the relationship is referred to herein as sliding contact between the guide members and the inner surface of the end walls of the rotor.

By providing integral with the vane units guide members which present a surface for sliding contact that is several times the width of the edges of the vanes 42a,;42b and 420, small clearances can be maintained between the vanes and the confin ing surfaces provided by end walls 23 and 29 and,

by sealing rings l6 and Hi without imposing frictional wear on the edges of the vanes. Thus when, as shown, the inner surfaces cf the sealing rings l6 and I6 are in alignment with the inner surfaces of end walls 23 and 29 of the rotor, the guide members protrude slightly beyond the edges of the vanes so that the guide members, by contact with the inner surfaces of end walls of the rotor, maintain the vanes, which extend through the rotor into the crescent shaped compression space about the periphery of the rotor, out-ofcontact with any surface but sufficiently close thereto to afford eificient operation of the apparatus. In this manner the seal provided between the edges of the vanes and the confining means is maintained effective for highly efficient operation of the apparatus and since the edges of the vanes are not subjected to wear the apparatus is capable of prolonged use without substantial impairment of emciency caused by poor sealing between the edges of the vanes and the confining means. The guide members present a sliding contact surface which ordinarily is about one inch in width in'the direction of the relative motion between the memher and the part in sliding contact therewith and which preferably is at least inch in width. It is apparent that the guide members provide guide means radially spaced from the vane unit bearings and from shaft 34 for axially confining the vane units. The shape and number of the guide members may be varied and the surface presented by a part integral with the rotor, or otherwise, for sliding contact with the guide members may be varied. It is desirable, however, that each of the vane units be guided independently of the others as in the embodiment shown. The guide members generally are composed of material that is different from the material of the surfaces in sliding contact therewith, the requirements being resistance to wearing rather than strength. In the ordinary case the end walls of the rotor are made of metal formulated so as to have high strength. In such case the guide members can advantageously be com posedcf a suitable bearing metal, for example. When, as in the illustrative embodiment of the invention that is described herein, the guide members are lubricated by means of water, it is preferable to employ for the guiding surface of the guide members a plastic material such as the plastic material described herein below for use in the vane unit and rotor bearings, namely, a plastic having a phenol-aldehyde resin as a base and containing asbestiform mineral fiber and graphite.

The lubricating means for lubricating the vane unit bearings and the rotor journal bearing also is a feature of this invention. In the embodiment shown, these bearings are lubricated by means of water. The water used for lubrication is fed in by the line 55 which is controlled by valve 56 and which preferably contains a fine mesh strainer 51 and a flow indicator 58. The bearings for the vane units are fed by the branch line 59 which The vane unit bearings are arranged so thatthe water fed into the bearings to act as a lubricant escapes therefrom and. becomes discharged accuser;

into the interior of the rotor; While the water remains on the interior of the rotor it effectively acts as a lubricant between the guide members 53 and the inner surface of the end walls of the rotor as well as between the pivot blocks 41 and the vanes 42a, 42b and 420. Adjacent the inner wall of the rotor segments 27 are passages 63- which constitute means for directing the water to the region outside of the rotor. The Water eventually escapes from the apparatus as will be described below in connection with the construction and operation of the sealing means.

For lubricating the rotor iournal bearing,.water. is taken from line 55 by branch lines 54 and 6-5, the latter line being tapped through bushing. 32 by connections 66 (Fig. to the arcuate passage 61 in the face of the bushing. Water escaping from. the journal bearing is discharged from the apparatus as will be described in connection with the sealing means.

The sealing means for effecting a vapor seal between the rotor and the confining means is provided by the outwardly extending recess 68 provided by seal plate i6 and the outwardly extend.-

ing recess 63' provided by the sealing plate 16''.

Carried by the rotor and integrally therewith, is the flange 69 which penetrates into recess 88 and, on the opposite side, flange which penetrates into recess 58'. The flange 6d is carried upon the rotor end wall 29, and, as shown in Fig. '7, one side of the flange has notches 7E3 cut therein leaving. fin-like projections along the edge of the flange that penetrate into the recess 68'. Similar notches are cut out of the flange 69. The notches provide impeller means for causing any liquid in the recesses 58 and 68' to be-thrust along by the movement of the flanges es and 5% thereby acquiring such centrifugal force as to maintain the recesses 68 and 63' filled with water regardless of. the position of the compressor.

Water escaping from the vane unit bearings and thence to the exterior of the rotor tends to flow outwardly into the recess 38, while water escaping from the rotor journal bearing tends to fiow outwardly into the recess thereby providing water for maintaining the liquid seal. It is preferable for the purpose of providing an assured source of liquid for the sealing. means to tap'the branch line 5 i directly through the front cover plate 25- so as to supply the recess 68, and: to tap a continuation of the line 55 directly through the back cover plate as shown. Preferably the bottom portion of recesses 68 and. 68 are provided with drain passages 'H and 'i I which can be plugged by plugs l2 and 72' during normal. operation of the apparatus.

During operation of the apparatus the water fed into the recesses 68 and E8 gradually flows into the chamber between the rotor and'the confining means and escapes as a mist with the com-- pressed vapor.

By lubricating the bearings for the vane units and the rotor journal bearing with water, which, of course, is the condensate of the vapor being. handled by the apparatus, the entire apparatus is simplified and one is able to avoid danger of contamination of the water vapor being handled by oil or other similar lubricant. If oil or other lubricant were used it would be necessary, in

order to-avoid contamination of the water vapor being handled by the apparatus,. to provide a. number of lubricant seals, about ten to twelve, and such seals together with conduits for directing lubricant to the bearings would add greatly: tor-the size, complexity and cost of the'equipment.v

8 Moreover, there would. be constant danger that onev or more of the: seals, due to wear, would be-' come defective with consequent contamination of the water vapor that is compressed by the apparatus.

Somewhat more generally according to this invention, bearing parts of the compressorpr motor apparatus are lubricated with liquid which is compatible with the gas or vapor being handled by the apparatus and which preferably is the liquid phase of the gas or vapor handled by the apparatus. Preferably the liquid used as lubricant is non-corrosive to the parts of the apparatus with which it is brought into contact and has a viscosity during operation of the apparatus which ranges from thatof. water to that of an oil having an S. A. E. viscosity of about 30. When such a lubricant is used, the lubricant may, as in the device shown, come into contact with the gases or vapors being handled by the apparatus and may be partially vaporized, the resulting vapors being commingled with the gas or vapor being handled by the apparatus.

The foregoing with regard tov the liquid usedfor lubricating the. bearing parts of the apparatus is likewise applicable to the liquid used for providing the liquid seal between the rotor and the confining means, namely, the liquid used for the liquid. seal should be compatible with the gas or vapor being. handledv by the apparatus and preferably the. liquid used should be the liquid phase of the gas or liquid being handled by the apparatus. a positive and effective seal is provided without the necessity for machining closely fitting parts and by means which minimizes friction andwean When a liquid is used inthe manner aforesaid as a lubricant for bearing parts of the apparatus or to provide a liquid seal, the liquid serves a further function, namely, that of cooling the working parts of the apparatus. In the ap paratus shown, and illustrated in connection with the compression of. steam, water being used to lubricate the bearings and provide a liquid sealbetween the rotor and the confining means, the working parts of the apparatus operate at substantially the boiling point of water, and since the clearances. provided are calculated for operation at thistemperature any overheating of some of the parts would. resultin binding of the apparatus so as to lower its efficiency if not stop it altogether. By passing a substantial flow of water through the apparatus, the flow of liquid from the inner parts of the apparatus to the outer parts tends tocarry heat from the inner working parts to the outer parts from which heat can escape more readily thus acting to prevent overheating of the inner parts. In addition, a substantial quantity of liquid that is used for lubricant and for the seal becomes vaporized and in becoming vaporized a considerable amount of latent heat of vaporization is taken up with resultant cooling effect upon the working parts of the apparatus. It is desirable that theliquid be flowed: through: the apparatus at the rate of at least gallon per minute and: preferably at the rate ofat least gallon per minute for apparatus capable of handling. ten pounds of vapor per minute when the apparatus; is used either as a compressor or as a motor. While it is preferable that the liquid that serves as a cooling medium likewise be employed as a lubricant or as a sealing. medium or both as described above, it is apparent that theiiquid may be. used solely as 5 acooling. medium for the working. parts in'- the By the use of such sea-ling meansinterior of the compressor or motor apparatus, the liquid preferably being introduced adjacent the bearing means for the rotor and the vane units so that the liquid will pass outwardly and carry heat from the central parts of the apparatus to the outer parts and thence to the surrounding environment.

In employing water as a lubricant for com pressor or motor apparatus used for handling water vapor as in the typical operation described, the water is preferably heated to approximately its boiling point before being introduced into the apparatus. Thus when the apparatus is part of a vapor-compression distillation unit used for recovering pure water, a part of the water distillate at substantially its boiling point may be removed fro-m the condenser and taken direct? 1y to the compressor or motor apparatusfor use as a lubricant. If some other source of water as lubricant is used, some suitable means for heating the water prior to directing it into compressor or motor apparatusmay be employed. so that the water will be heated tosubstantially its boiling point or to at least about 200"v F. For example, the water may be heated in the reservoir 16 by some heating device such asheating'coil 'I'l through which some heating medium such as steam or hot exhaust gases may be passed. At its boiling point water has a much lower viscosity (about .284 centipoise at 212 F.) than it does at ordinary temperatures (about .981 centipoise at 70 F.). Notwithstanding'the low viscosity of the Water at'elevated temperatures, thewater has been foundto provide satisfactory-lubrication for the apparatus .of this invention.

In using liquids other than wateras lubricant the apparatus with which the liquid comes'into contact. It is preferable, however, thatthe .liq-

-uid used as lubricant be introduced into the apparatusat approximately the normal operating temperature of the apparatus, which ordinarily is approximately the boiling point of the liquid used as lubricant. I

In the operation of the compressor or motor apparatus of this invention with means for sup plying water as a lubricant for the bearings, it has been found that ordinary bearing'metals are inadequate. When,for example, the compressor or motor apparatus is used as acompressor for steam where both the lubricant (water) and the parts to be lubricated are maintained at a temperat-ure which is substantially the boiling point of water, experiments have shown that most materials, when subjected to test for bearing 'use undersuch conditions, are inadequate for the purpose. I have found that by employment of certain combinations of materials for the bear-' 'ing surfaces of the relatively movable bearing members, satisfactory operation under the conditions referred to can be obtained. The preferred combination consists in employing nitrided Nitralloy. as the bearing surface presented byone of the bearing members and employing as the bearing surface presented by the other'bearing member a rigid material having synthetic phenol aldehyde resin'as a base, and containing asbestiform mineral fiber and graphite. Nitrallo y is the bearing surface of another bearing member havin synthetic phenol-aldehyde resin as a base and containing asbestiform mineral fiber and graphite, affords a new bearing which is capable of use under conditions that cause excessively 'rapid deterioration of bearings of the kinds heretofore employed.

Another suitable bearing which I have found to be suitable for withstanding the severe condi} tions mentioned -above consists in the combination of a bearing member presenting a bearing surface having a synthetic phenol-aldehyde resin as a base and containing asbestiform mineralfiber and graphite with a relatively movable bearing member present ng a bearing surface consisting of high silicon Monel metal. Monel metal is a, substantially non-ferrous alloy con-'- taining 60% to% nickel, 25% to 35% copper, lj% to 3% iron, 0.25 to 2% manganese, 0.02% to 1.5% silicon, and 0.3% to 0.5% carbon. By reference herein and in the claims to high silicon Monel metal', the reference is to Monel metal which contains about 4.0% or more of silicon. Other metals having a Brinell hardness above 200 and preferably above 300 that are not corroded by the action of water at its boiling point and by steam may likewise be employed .in combination with the non-metallic part of the bearing although the two alloys specifically mentioned are preferred. In the bearing member which presents a bearing surface having a synthetic phenol-aldehyde resin'as a'base and containin asbestiform min- I eral fiber and graph te, the graphite acts as a lubricant. Another solid lubricant which may be employed in lieu of or in addition to graphite is mica flakes. However, the employment of graphite as the major proportion of the solid lubricant is preferable. While asbestiform m neral fiber is preferred, other mineral fibers such as rock-wool or glass fibers may be employed. Another resinous material that may be employed is a hard'synthetic resin of the melamine tvpe, although'resins of phenol-aldehyde type which are hardiand highly resistant to boiling'water are'j'preferred. A resin or a metal that withstaridsboiling water for as long as one week without apparent change is regarded as having high resistance to boilin water.

1 Referring more s ecifically to the em odiment' of this invention shown in the drawings and' described here nabove, the shaft 34 preferably is composed of nitrided Nitralloy and the bushings 40a, 46b. and 400 may be composed essentially of synthetic phenol-aldehvde resin, as bestiforin mineral fiber and graphite. Alterna- .tively the shaft 34" may be composed of high silicon Monel metal. Similarly, the journal bearing 3! may be composed of n trided Nitralloy or "hi h silicon Monel metal and the journal bearing bushing 32 may be composed of the syn th'etic -phenol aldehyde' resin containing asbesti for'rn'mineral fiber and graphite. I

While the novel bearing above described is of particular advantage when embodied in compressor or motor apparatus of the character described, it is apparent that it is of general advantage and utility for use under special severe conditions such as those encountered when a bearing is operated at relatively high temperature using a liquid such as water as a lubricant.

In operation of the apparatus as a compressor for the compression of steam, the rotor may be rotated in a counterclockwise direction (Fig. 3) by the power shaft H. The rotation of the rotor causes the vanes to be rotated therewith thereby sweeping the vapor into the crescent shaped chamber which, in the region of the inlet l8, becomes of increasing cross-sectional dimensions in the direction of rotation of the rotor. The vapor then becomes entrapped between the vanes in the region between the inlet and outletports, and since the crescent shaped chamber becomes of decreased cross section as it approaches the exhaust port E9, the vapor is compressed and, when it reaches the exhaust port, will have become compressed to the desired pressure to be maintained at the exhaust port. During operation clean water, which ordinarily is distilled water when the compressor constitutes part of a vapor-compression distillation unit for the distillation of water, is supplied to the vane unit and rotor bearings and to the sealing channel. For a compressor handling about 280 cubic feet per minute of steam at approximately atmospheric pressure, the water may, for example, be fed at the rate of about one-half gallon per minute as indicated by the flow meters 58. The water provides lubrication for the movable parts with the exception .of the power shaft H, and provides liquid for the sealing channel. It is to be noted that lubrication is afforded while avoiding any possible source of contamination of the steam with vapor or entrained liquid derived from lubricating oil. This is of considerable practical importance, when, for example, the steam is subsequently condensed to provide distillate to be used as drinking water.

It is apparent that if steam under elevated pressure, e. g., as supplied by a boiler, were to be introduced at the port I9 (which in such case would become the inlet port), the port is being maintained in communication with a region of lower pressure, the rotor and vanes would be rotated in a clockwise direction and the shaft II would become a power shaft from which power could be taken off.

While this invention has been described in connection with a specific embodiment and application thereof, it is to 'be understood that this has been done merely for the purpose of illustration. Generally, "however, this invention is of particular advantage and utility in compressor or motor apparatus for handling vapor and gases through a relatively low compression or expansion ratio. The features of this invention relating to liquid lubrication, sealing and cooling are of particular utility and advantage when the compressor or motor apparatus is used to handle a gas or vapor which is compatible with the liquid'used for lubrication, sealing or cooling purposes, and preferably whenthe apparatus is used to handle a vapor, the liquid used for lubrication, sealing and cooling purposes is the liquid phase of the material in vapor form that is handled by the apparatus. In this connection i y inQ ki i ned that when the apparatus is used for handling air, water can sat sfactorily be used for lubrication, sealing and cooling of the apparatus. ,If desired a liquid-vapor .separator can be used to separate any entrained droplets of the liquid used for lubrication, sealing or coolingpurposes from the gas or vapor discharged from the apparatus, but ordinarily this is not necessary or desirable.

The compressor or motor apparatus of this invention may, if desired, be designed for use with more than three vane units. The principal advantage of using more than three vane units is to attain a higher compression or expansion ratio between the inlet and outlet ports. In compressor or motor apparatus utilizing three vane units the maximum compression ratio is about 1 to 2.5. By utilizing ten vane units, the maximum compression ratio can be increased to about 1 to 16. A compressor or motor apparatus embodying this invention is highly desirable for use as the compressor unit in vapor-compression distillation equipment adapted for caus ing vaporization of solution in a vaporization chamber, compressing the evolved vapor by a compressor to a pressure at which the condensing a temperature of the compressed vapor is above the boiling point of the solution in the vaporization chamber, and directing the compressed vapor for condensation in out-of-contact heat exchange relation with the solution in the vaporization chamber. For such use a compression ratio of the order of about 1 to 1.2 is all that is required, and the employment of a compressor of the character herein described which has three vane units is generally adequate. While the capacity of a compressor or motor unit is somewhat increased by increasing the number of vane units, the advantage of the small increase in capacity is usually offset by the increased .cost of providing additional vane units and it is generally desirable to employ the minimum number of vane units required for attaining the desired compression or expansion ratio to be maintained.

The compressor or motor apparatus may be supported in other ways than the manner shown and described ghereinabove. Moreover, the power shaft connected to the rotor may be arranged other ways. Thus the support Ill instead of being an integral part of some other unit may merely serve as a bearing support for. the shaft ll so that the compressor or motor unit will be complete in itself and readily adaptable for use with any source of power or with any mechanism to be driven. In preferred practice, however, and accordin to one of the features of this invention, the power shaft ll of the compressor or motor apparatus is integral with the power shaft of an engine so that the rotor is rigidly secured to the power shaft of the engine. In such case the engine comprises a suitable support for the engine power shaft, and bearing means are provided for rotation of the power shaft of the engine in fixed relation to the support. The confinin means of the compressor or motor is in turn rigidly secured to the support for the power shaft of the engine so that the support for the power shaft of the engine also acts as the support of the confining means of the compressor or motor. In the embodiment herein shown and described by way of illustration, the rotor of the compressor or motor is rigidly secured with the crank shaft of an internal combustion engine and acts as a flywheel for the engine crank shaft while the confining a 9f the compressor or motor is rigidl sehave been largely overcome.

cured with the crank case of the internal combustion engine in which the crank shaft rotates in fixed relation by means of suitable bearings such as bearing 15. Heretofore difficulties have been encountered in the operation of rotary compressors due to failures of the driving mechanism. Such failures are due largely to inability to maintain the driving and driven parts in proper alignment under conditions of engine vibration and prolonged periods of operation. To overcome such difficulties resort has been made to the use of flexible couplings between the compressor and the engine for supplying power to the compressor, but such flexible couplings not only have not completely remedied the difficulty but also have in themselves been a frequent source of failure. By mak ng the rotor of the compressor or motor rigidly secured with the engine power shaft and making the confining means of the compressor or motor rigidly secured with the support member for the engine power shaft, such difficulties With such combinaton the alignment is established as a factory operation rather than in the installation and coupling of separate units on the job, and the parts are so rigidly connected that misalignment resulting from abuse and prolonged periods of operation is much less l kely to occur.

In addition to the foregoing, it is apparent that other modifications and variations may be made in the construction and operation of the compressor or motor apparatus of this invention that has been described and shown herein by way of illustration without departing from the scope of this invention as defined by the language of the following claims.

Iclaim:

1. In compressor or motor apparatus of the character described includ ng confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means for mounting sa d rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition w th a limited portion of the inner surface of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely to said rotor and extending through the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner surface of said confining means to provide barriers extendng across said crescent shaped chamber, and means for mounting said vane units for rotation with said rotor about a fixed axis coincident with the ax s of said cylindrical surface of said confining means; guide means for guiding said vane units,

said guide means comprising a slidable contact member spaced from the axis of rotation of said vane units and carred on each of the opposite edges of said vane units in sliding contact with each surface respectively of opposed parallel confining surfaces rigid with said rotor and normal to the axis of rotation of said rotor.

2. In compressor -or motor apparatus of the character described including Iconfining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means for mounting said rotor for rotation about an. axis that is offset from the parallel to th axis of '14 said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of the inner surface of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely to said rotor and extending through the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner surface of said confining means to provide barriers extending across said crescent shaped chamber, and means for mounting said vane units for rotation with said rotor about a fixed axis coincident with the axis of said cylindrical surface of said lconfining means; guide means for guiding said vane units, said guide means comprising slidable contact members carried by said vane units on opposite sides of the rotational axis of said vane units and radially spaced therefrom and on opposite edges of said vane units in sliding contact with opposed parallel confining surfaces rigid with said rotor and normal to the axis of rotation of said rotor.

3. In compressor or motor apparatus of the character described including confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means for mounting said rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of the inner surface of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely to said rotor and extending through the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner surface of said confining means to provide barriers extending across said crescent shaped chamber, and means for mounting said vane units for rotation with said rotor about a fixed axis coincident with the axis of said cylindrical surface of said confining means; guide means within said rotor for guiding said vane units, said guide means c0mpris-, ing a slidable contact member on each of the opposite edges of said vane units and on the remote side of the axis of rotation of said vane units from the portions of said vane units that extend through said rotor, and confining means cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of the inner surface of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, aplurality of vane units disposed transversely to said rotor and extending through the periphery of said rotor'in slidable relation thereto and terminating in close cps-gem 15 proximity to the inner surface of said confining means to provide barriers extending across said crescent shaped chamber, shaft means the axis of which is coincident with the axis of said cylindrical surface of said confining means, and bearing means integral With said vane units for mounting said vane units for rotation about said shaft means; guide members carried on opposite edges of said vane units and on each side of said shaft means radially spaced from said bearing means, said rotor being provided with end walls presenting an inner surface of said rotor that is disposed for sliding contact with said guide members.

5. In compressor or motor apparatus of the character described including confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means for mounting said rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of the inner surface of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely to said rotor and extending through the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner surface of said confining means to provide barriers extending across said crescent shaped chamber, shaft means the axis of which is coincident with the axis of said cylindrical surface of said confining means, and bearing means integral with said vane units for mounting said vane units for rotation about said shaft means; guide means within said rotor and radially spaced from said bearing means for axially confining said vane units during rotation of said vane units about said shaft means, said rotor comprising end walls presenting spaced opposed parallel surfaces normal to the rotational axis of said rotor and said guide means comprising a contact member which is carried by each of the opposite edges of said vane units for sliding contact with each of said opposed surfaces respectively and which is substantially wider than the vane unit edge guided thereby,

6. In compressor or motor apparatus of the character described, said apparatus including confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means for mounting said rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of said confining means between said inlet and outlet ports leaving a crescent shaped chamber be tween said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely of said rotor and extending through openings in the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner cylindrical surface of said confining means to provide barriers extending across said crescent shaped chamber, shaft means in fixed relation to said confining means having its axis coincident with that of the inner cylindrical surface of said confining means, and bearing means integral with said vane units for mounting said vane units for rotation about said shaft means; guide means within said rotor for guiding said vane units including guide members carried by said vane units spaced from said bearing means in slidable relation with opposed parallel surfaces normal to the rotational axis of said rotor and presented by the end walls of said rotor, means for directing liquid to said bearing means to provide lubrication therefor, said bearing means being adapted to permit escape of said liquid therefrom to the interior of said rotor thereby providing lubrication for said guide means, sealing means for said crescent shaped chamber adapted to provide a seal between the periphery of said rotor and said confining means, said sealing means comprising flange means integral with said rotor at the periphery thereof disposed radially outwardly relative to the rotational axis of said rotor and annular channel means integral with said confining means and disposed for outof-contact penetration of said annular flange means therein during rotation of said rotor relative to said confining means, and means for directing liquid from the interior of said rotor to said annular channel means.

"'7. In compressor or motor apparatus of the character described, said apparatus including confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means .for mounting said rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely of said rotor and extending through openings in the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner cylindrical surface of said confining means to provide barriers extending across said crescent shaped chamber, shaft means in fixed relation to said confining means having its axis coincident with that of the inner cylindrical surface of said confining means, and bearing means integral with said vane units for mounting said vane units for rotation about said shaft means; means for directing liquid to said bearing means to provide lubrication therefor, said bearing means being adapted to permit escape of liquid therefrom to the interior of said rotor, sealing means for said crescent shaped chamber adapted to provide a seal between the periphery of said rotor and said confining means, said sealing means comprising flange means integral with said rotor disposed radially outwardly relative to the rotational axis of said rotor and annular channel means integral with said confining means and disposed for out-of-contact penetration of said annular flange means therein during rotation of said rotor relative to said confining means, and means for directing liquid from the interior of said rotor to said annular channel means.

8. Apparatus according to claim 7 wherein there is supplemental means independent of said bearing means for supplying liquid to said annular channel means.

.9. In compressor or motor apparatu of the character described including confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a

, rotor within said confining ineans, means for mounting said rotor. for rotation about n axis that is ofiset from and parallel to the axis-of said cylindrical surface of said confining means with the periphery. of .said rotorf in juxtaposition with alimited portionofthe inner surface of's'aidc'onfining means between said inlet .and outlet ports leaving a crescent shaped chamber between said rotor and said. confining means, a power-shaft connected to saidrotor, a plurality of vane units disposed transversely t6 said rotor and extending through openings in the periphery of said rotor slidable relation thereto and terminating in close proximity-to the-inner cylindrical surface of said confining means'to provide barriersextending; across f said crescent shaped chamber, and

means for-mounting said vane units for rotation said rotorabout-a fixed axis-coincident the -axis of said cylindr'icalsurface of s a-idconfining me'ans;--sealin-g means for said'crescent shaped chamber adapted to provide a seal between the periphery of said rotor and said confining means, said sealing means comprising annular flange means integral with said rotor at the periphery thereof disposed radially outwardly relative to the rotational axis of said rotor, annular channel means integral with said confining means disposed for out-of-contact penetration of said annular flange means therein during rotation of said rotor relative to said confining means, and means for supplying said channel means with a liquid.

10. In compressor or motor-apparatus according to claim 9, said annular flange means being provided with projections adapted to impel liquid in said channel means along said channel means in the direction of movement of said flanges in said channel means.

11. In compressor or motor apparatu of the character described including confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a rotor within said confining means, means for mounting said rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of the inner surface of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a power shaft connected to said rotor, a plurality of vane units disposed transversely to said rotor and extending through openings in the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner cylindrical surface of said. confining means to provide barriers extending across said crescent shaped chamber, and means for mounting said vane unit for rotation with said rotor about a fixed axis coincident with the axis of said cylindrical surface of said confining means; sealing means for said crescent shaped chamber adapted to provide a seal between the periphery of said rotor and said con fining means, said sealing means comprising an annular channel adjacent each side of said cylindrical inner surface of said confining means, each said annular channel being disposed in a plane normal to the axis of said rotor and being disposed outwardly relative to said inner surface of said confining means and radially about the axis of said rotor, an annular fiange integral with each side of said rotor, each said annular flange being at the periphery of said rotorand penetrating into one of said annular channels in zout-of-contactrelation: thereto, and means for supplying said channels with a liquid to providea seal at said channels between said confinin means and said rotor during rotation of said rotor relative to said confining means.

12. In compressor or motor apparatus of the character described comprising a confining member and a rotor member that is rotatable relative to said confining member, sealing means for providing a: seal between saidconfining member and said rotor member, said sealing meanscomp'rising annular channel means carried by one of-said,

members extending radially outwardly from the axis otro'ta'tionof said rotor, means for-supplying-said channel means with a liquid, anannular sealing part carried-by the otherof said members and disposed-radiallyoutwardly. from the axisbf rotation of said motor for penetration 4 into i said channel means i-n-out=of-'contact relationi'with said channel -means and-meansf'o'r movingcsaid liquid so as to maintain said liquid in said annular channel means by centrifugal force.

13. Compressor or motor apparatus of the character described comprising confining means having spaced inlet and outlet ports therein and presenting an internally cylindrical surface, a

rotor within said confining means, mean for mounting said rotor for rotation about an axis that is offset from and parallel to the axis of said cylindrical surface of said confining means with the periphery of said rotor in juxtaposition with a limited portion of said confining means between said inlet and outlet ports leaving a crescent shaped chamber between said rotor and said confining means, a plurality of vane units disposed transversely of said rotor and extending through openings in the periphery of said rotor in slidable relation thereto and terminating in close proximity to the inner cylindrical surface of said confining means to provide barriers extending across said crescent shaped chamber, shaft means in fixed relation to said confining means having its axis coincident with that of the inner cylindrical surface of said confining means, bearing means integral with said vane units for. mounting said vane units for rotation about said shaft means, annular flange means integral with said rotor at the periphery thereof disposed radially outwardly relative to the rotational axis of said rotor, annular channel means integral with said confining means disposed for out-of-contact penetration of said annular flange means therein during rotation of said rotor relative to said confining means, and means for directing a flow of liquid from the exterior of said rotor into said channel means and from said channel means to the interior of said chamber for expulsion from the apparatus with gas or vapor passing through said chamber between said inlet and said outlet ports.

14. Compressor or motor apparatu according to claim 13 which also comprises means for heating said liquid prior to its being directed into said channel means.

15. In a rotary compressor adapted for the compression of a gas or vapor, sealing means providing a liquid seal between a stationary part and a rotatable part, said sealing means comprising an annular channel rigid with said stationary.

into said channel in out-of-contact relation I therewith, and means for supplying said channel with liquid, said sealing member being adapted" ALLEN LATHAM, JR.

. REFERENCES CITED --The following references are of record in the fi l'e of this patent:

" UNITED STATES PATENTS Name Date Jamieson Dec. 18, 1877 Baker Nov. 11, 1890 Green Apr. 27, 1897 Reichhelm Oct. 23, 1900 Been Mar. 21, 1916 Miller July 4, 1916 Hay Feb. 1, 1921 Wood Feb. 8, 1927 Viamello Mar. 25, 1930 Edwards -1 Sept. 19, 1933 Number 9 Number Name Date" Gette Mar. 12, 1935 Moffitt June 11, 1935 Johnson Jan. 7, 1936 Hollander Feb. 2, 1937 Haydocket et a1. Feb. 16, 1937 Smith July 9, 1940 Fulcher June 3, 1941 Jawarowski et a1. Feb. 5, 1946 FOREIGN PATENTS Country Date a Great Britain 1830 Great Britain 1906 Great Britain Nov. 13, 1908 Switzerland June 1, 1932 Great Britain June 7, 1934 France Dec. 7, 1910 Great Britain Mar. 22, 1939 France Dec. 27, 1932 Certificate of Correction Patent No. 2,536,851 January 2, 1951 ALLEN LATHAM, J R.

It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows:

Column 5, line 21, for blocks 37 read blocks 47' line 53, for the word guides read guide; column 9, line 21, after into insert the; column 11, line 35, tor meters read meter; column 12, line 25, strike out a before temperature and that the said Letters Patent should be read as corrected above, so that the same may conform to the record of the case in the Patent Oflice.

Signed and sealed this 8th day of May, A. D. 1951.

THOMAS F. MURPHY,

Assistant Uommissz'oner of Patents. 

